Vapor compression apparatus



April 18, 1961 A. c. SAMPIETRO 2,979,921

VAPOR COMPRESSION APPARATUS Filed Aug. 4, 1958 2 Sheets-Sheet 1 H Ac/uY/es C. Samp/efro April 18, 1961 A. c. SAMPIETRO 2,979,921

. VAPQR COMPRESSION APPARATUS I Filed Aug. 4, 1958 2 Sheets-Sheet 2 A 2; 14 K l/ 78 f 10 11 JUTO ENG/IVE J7 7 i? g. 5

AcfiH/es C. Samp/ezm n akm.,%m; QM/1Z iggr United States Patent VAPOR COMPRESSION APPARATUS Achilles C. Sampietro, Detroit, Mich., assignor to Thompson Ramo Wooldridge Inc., a corporation of Ohio Filed Aug. 4, 1958, Ser. No. 752,801

Claims; Cl. 62-428) circumferentially stacked relation with respect to one another, thereby promoting greater efliciency in construction and operation. I I 7 Another object of this invention lies in the provision of a refrigerating and air-conditioning unit which is susseptible of wide variations in compressor construction -to fulfill particular requirements. 7

Another object of the invention is to provide a vapor compression apparatus wherein motivation therefor may be provided by a single source connecting with shafting at either end of the apparatus, and in automotive applications, may be provided by connecting a power source to one end of the shafting to actuate said apparatus during movement of the vehicle and by connecting the opposite end of the shafting with an auxiliary power source to be employed when the main power source is not-in use. I

. 2 in accordance with the present novel concepts embodies a common shaft driven by a suitable prime mover and supporting communicating compressor, condenser and evaporator chambers, the compressor in one form of the invention housing a cylinder receiving piston reciprocated by roller or equivalent means traveling upon a stationary cam surface. Fluid inlets are provided in the cylinder walls, and the shaft interior carries valve means porting compressed refrigerant to a spirally shaped condenser embedded in cooling fins over which an air streamis drawn by fan means integral with the rotating apparatus. The fins are passaged to discharge the fluid into an annular receiving chamber circumferentially surrounding the condenser and mounting therewithin a syphonpro vided to port centrifugally forced liquidadjacent the walls of the receiving chamber into an annular evaporator communicating with the suction chamber of the compressor. Low pressure 'fiuid produced in the evaporator is cooled by radially extending fins against which an air stream is directed by fan means integral with or separate from the rotating apparatus. 1 t 3 Modifications may readily be effected in the compressor and communicating condenser and evaporator to meet a particular set of requirements. By way of example and not by limitation, the reciprocal piston and stationary cam arrangement may be replaced by a compressor construction embodying a centrifugal impeller. 'In a preferred form of this particular construction; a rotatable compressor chamber rigidly mounts interiorly thereofa carrier supporting a pair of planetary gears meshing with a ring gear stationary with an impeller housing. A sun gear mesheswith the planetary gears and connects with the impeller to drive the same. Torque reaction on the stationary ring gear is counterclockwise, while the reaction on the compressor scroll is clockwise. Accordingly, the weight need furnish only the difference between the two reactions as a restraining torque. Other structural features of the present invention will be specifically A further object of the present invention lies in the provision of a rotary refrigerating apparatus in which controlled flow of condensate into evaporative heat exchange means is eifected by a syphon device positioned with one end in communication with centrifugally impelled liquid refrigerant.

A still further object of this invention is to 'provide a heating or cooling construction wherein forced air flow over condenser and evaporator means may be readily effected by fair means integral with the rotating apparatus.

Other objects and advantages of this invention will become more apparent during the course of the following description, particularly when taken in connection with the accompanying drawings. I

In the drawings, wherein like numerals are employed to designate like parts throughout the same:

- ratus performing the functions ofrefrigerant compression", 1

Figure 1 is a vertical sectional view, with parts in elevation, of a vapor compression apparatus constructed in accordance with the principles of the present invention;

Figure 2 is a schematic illustration of the present refrigerating apparatus in association with motivating means thereforr' Figure 3 is a sectional view of the'compressor chamber of Figure l, and further showing 'cam means therein to effect piston movement and compresion of the refrigerant;

Figure 4 is a sectional view of a modified form of compressor means embodyingthe principles of this invention,

and particularly illustratiriga centrifugal ir'npeller and related structure to effect refrigerant compression; and 1 of Figure. 4.

Figure 5 is an end viewof the compressordrivemeans referred to during the course of the description now to follow, and additionally, variousmodifications falling within the purview of. the present invention will be 'apaccordingly'be described inthat connection-herein; Re- I ferring now first to Figure 2, a vaporcompression appacondensation and evaporation is designated therein generally by'the legend A. The apparatus A is rotated as avunit'upon 'shafts 10 and 11'extendingaxiallyfrom oppo [site ends thereof, and' as sh'own,'either one or both of the shafts 10 and 11 may have connectedtheretoa suitable -power-source.' In automotive applications, for ex ample, rotation of the shaft 11 and corresponding rotative movement of the apparatus A may be effected by connection through overrunning clutch means 12 and ashaft 13 to the main engine of the automobile. Alternatively, the

drive means for "the shaft 11 may comprise arturbine to which oil under pressure is furnished by an engine, transmission, or. vehicle driven pumpSuch a pumpmayjin some instances-be the power steering pumpv or the front pump inthe automatic transmission. As a further al ternat ve, the motion of the automotive vehicle may-be employed .to. drive the shaft'll and supported refrigereat'i'ng'unit A. 1'

r 7 Should itf be desiredtoobtain the benefits ofthe'appa :ratus A when the-vehicle.is-istationary or the mainiengine I, ths st .td .'.a=-9Qn ary sourceot powerffor the-unit meral 42.

a -a ar.

Aisprovided and this may take the form of a motor 14 connecting through a shaft 15 with overrunning clutch means 16 operative with the shaft 16 On the other hand, a relatively small engine connecting with a suitable source of current may be employed as the motivating means for the compression refrigeration apparatus; of the present'invention.

Specific structural features of an exemplaryembodiment of a heating and cooling unit A are shown in Figures 1 and 3 and reference is now made thereto. The

. apparatus is cast or otherwise formed as a single integral unit to be supported upon and rotatable with the shafts 10 and 11, and a particular configuration presents a generally cylindrical outline in plan or section and a generally circular outline in end view. Provided at one end of the apparatus is a compressor housing 17 defining therewithin a chamber 18 containing a predetermined volume of refrigerant, which preferably is a fluorinated and/or chlorinated hydrocarbon and may be one of the Freon, compounds. In fluid communication withthe compressor chamber 18 and structurally integral with the housing 17 thereof is a condenser 19, which may be of the spirally Wound type embedded in an annular core 20 fixedly mounted on the shaft it The core 2% surrounding the condenser 19 is provided with fins 21 integral with an annular wall 22 defining on its outer circumference one surface of a receiving chamber 23 having a common wall 24 and in communication with'an evaporator chamber 25 formed on its outer circumference with a plurality of radially extending cooling fins 26.

The compressor housing 17 is cast or otherwise formed along one'wall 27 thereof with an axially extending embossment 28 at the radial center of the wall 27 and bored or otherwise passaged at 29 to receive in rigid securement the shaft 11. The opposite end of the shaft 11 is. firmly secured within a collar 30 formed integral withan opposite Wall 31 of the housing 17, the collar 30 being provided with a shaft receiving, bore 32.

Axially inwardly of opposite ends of the shaft 11 and preferably integral therewith is an open-ended cylinder 33. passaged with a pair of annular inlet ports 34 and 35 generally obliquely or diagonally cut around the cylinder circumference and communicating with the compressor chamber 18 and interior of said cylinder 33. If desired, valve means may be employed in connection with the inlet ports 34 and 35.

Functioning to compress refrigerant directed to the cylinder interior through the inlet ports 34 and 35 are a pair of freely mounted pistons 36 and 37 reciprocably movable-in slidable contact with the cylinder inner wall. Each piston axially inwardly of one end wall is bored entirely therethrough with a transversely extending;cylin-.

' drical opening 38 receiving pin means 39 mounting thereon roller means 4t rotatable Within a generally circular axially extending cavity 41 in each of the pistons 36 and 37. In substitution for roller means shown, a ball shape or equivalent configuration may be utilized, and inaddition, particular applications may'dictate that ball-type pistons are preferable to the cylindrical pistons illustrated. Providing a traveling surface for the roller meansd-il to accomplish reciprocation of the pistons 36 and 37 is stationary cam means designated generally by the nuan exterior configuration which is generally elliptical and interiorly thereof presents a true elliptical configuration. Accordingly, by reason of the outer circumference of thecam means not being a true ellipse, while the inner circumference or surface is truly elliptical, there isproyided a lower portion 43 of substantially greateryvall thickness than the remaining wall portion 44 and an out of, balance condition is created which causes the rela- As appears in Figure 3, the cam means has tively thicker portion 43 to depend and the 'ca-m'means 42; to remain essentially stationary when freely supported upon the shaft 11. It is to be further noted that-side sure faces- 45 and" 46 of the cam; means are essentially. flat 4 I andparallel withrespect to one anothenandthatthe outer circumferential surface 47 of said cam means is disposed at generally right angles to the side surfaces 45 and 46. The inner diameter of the cam means, on the other hand, is shaped to provide a central fiat camrning surface 48 against which the roller means 40 is in traveling contact, whileoutwardly of the surface 48 the inner diameter of the cam means is tapered or inclined as indicated at 49.

The cam structure 42 is preferably supported upon the shaft by means of a plurality of rib or spoke ,members 50 connecting at one end with the side surfaces 45 and 46 of the cam means and at their opposite ends with a hub or collar portion 51. The axially spaced, collar portions 51 support bearing means 52 restrained against displacement by said hub portions and an abutting surface 53 formed on the integral shaft and cylinder structure.

It may now be seen that by virtue of the configura tion of the cam means 42 and its free support with re spect to the rotating shaft 11, and cylinder 33 integral with said shaft, that the cam means being out of balance remains in an essentially stationary position. To avoid an interference with this condition, a clearance space or gap 54 exists between the surface 47 of the cam relatively thicker portion 43 and the inner diameter of the compressor casing 17.

At the end of the full compression stroke of each piston 36 and 37 said pistons are axially spaced from one another as indicated at 55 in Figure 1. During slidable in-v ward reciprocal movement of the pistons 36 and 37 in sliding contact with the inner walls of, the cylinder 33, refrigerant iscompressed between the inner. faces, of the pistons and forced axially into an outlet opening 56 extending axially of one end ofthe shaft 11 and radially inwardly of the inlet ports 34 and-35. Connecting with the opening 56 is a delivery passage 57 also extending axially of the shaft 11 and within said passage 57' ad: jacent the opening 56 suitable valve means 53 are provided. The valve means may comprise spring means59 bottoming at one end against a restraining ring, 60 secured within the shaft and at its opposite-end against a diaphragm member 61. ,It. may thus be seen that during a compression stroke of the pistons 36 and 37 mediaphragm member 61 moves axially in oppositionto the spring means 59 to, permit delivery of compressed fluid to the condenser 19, a portion 62' of which is surrounded by sleeve means 63 received within the passage 57 of the shaft 11.

While various forms of condensers are eifective for the present, purposes, particularly desirable results are obtained by use of the-spirally wound heat exchange means 19 shown. It may be seen that the condenser comprises a plurality of axially spaced coil segments. 64 embedded in the annular core 20, secured to theshaft 10 for'rotation therewith. Refrigerant vapor compressed to a high pressure condition by action of the pistons as and 37 in the chamber 18 is forced along the flow path indicated to the condenser 19 in which the vapor condenses, rejecting sensible heat from work doneupon it during compression plus its latent heat of vaporization.

To improve the efficiency of the heat exchange which takes place in the coil segments 6 30f the condenser 5' the core 29 is formed with a plurality of radially extend ing, tapered fins 21 over which powerful streams. of air are directed by a plurality of .fan blades. 65 extending radially from the collar portion 300f the compressor housing 17. A suitable mode of attachment is employed for the fan blades 65, and one ielfective ;manner isto ,cast said; blades; With..the-' compressor housing and end stricted passage 68 is formed through a portion of its length in an annular wall 69 with which the fins 21 are integral.

The annular receiver chamber 23 is thus defined by an annular outer wall 24, an'annular inner wall 69, an end wall 66 and an opposite end wall 70. Supported by the wall 24 common to the receiver and evaporator chambers is syphon means 71 of generally inverted J configuration having an open end 72 spaced radially inwardly of the wall 24 and an opposite end 73 spaced radially inwardly of an annular outer wall 74 of the evaporator chamber 25. The end 72 of the syphon means 71 is spaced from the wall 24 a predetermined distance calculated to receive condensate centrifugally impelled toward the wall 24 during rotation of the refrigeration apparatus A. Accordingly, when the level of condensed refrigerant held by centrifugal forces against the wall 24 reaches a particular level, said condensate is received in the open end 72 of the syphon and discharged into the evaporator chamber 25 through the opposite open end 73 of said syphon means.

The evaporator chamber 25 is of annular shape and defined by the wall 24 common to the receiver chamber 23, an end wall 67, an annular outer wall 74 and an end wall 75 opposite to the end wall 67. The evaporator chamber 25 receives through the syphon means 71 a liquid-vapor mixture from the receiver chamber 23 wherein, by reason of the pressure drop across the restricted passage 68, a sufficient portion of the refrigerant vaporizes to reduce the temperature of the remaining liquid to that consistent with the lower pressure. Within the vaporator chamber 25, on the other hand, the liquid-vapor mixture absorbs heat equivalent to the latent heat of vaporization of that portion of the refrigerant existing as liquid. The resulting low pressure vapor, from the evaporator then passes through an axially extending opening or passage 76 formed in an annular wall portion 77 integral with the wall 67 of the evaporator chamber and the wall 31 of the compressor housing 17. There is thus free communication between the evaporator chamber 25 and the suction side of the compressor chamber 17, and the low pressure vapor passing through the opening 76- is returned to the compressor chamber and the described cycle repeated.

Extending radially outwardly from the evaporator chamber wall 74 and axially spaced with respect to one another are a pluralityof tapered cooling fins 26. Directed into heat exchange relation .with the fins 26 is a stream of air produced by suitable fan means. The fan means may take various forms, and may comprise a fan an integral structural relationship between the compres sor, condenser and evaporator arranged to rotate as a single unit. The arrangement of pistons 36 and 37 reciprocal within-the cylinder 33 by action of roller means upon the cam means 42 is of high efiiciency sufficient to adequately fulfill the heating or cooling requirements of an average automobile. However, for larger installations different forms of compressors may be utilized and an exemplary centrifugal compressor is shown in Figures 4 and 5 to which reference is now made.

In the latter arrangement, the condenser, receiver and evaporator chambers are constructed in the same manner as shown in Figure 1, and accordingly have not been illustrated in full. Further, to house the compressor structure of Figures 4 and 5, a housing 79 is provided of generally similar construction to the housing 17 of Figure l. The housing 79 is generally circular when viewed in end, and is provided with an end wall 80 apertured at 81 substantially centrally thereof and a collar portion 82 formed to support within the aperture 81 a shaft 83 which connects in the manner earlier described with an automobile engine or other prime mover. Fan blades 84 are secured to the housing end wall 80 by being cast with the housing 79 or attached thereto in any other suitable manner. ously noted to direct streams of air across the fins extending radially from the evaporator chamber.

Secured to the inner surface of the housing end wall 80, and if desired also to theend of the shaft 83, is a plate member 85 which functions as a planet carrier. Adjacent opposite ends of the planet carrier is a pair of pin or shaft means 86 and 87 mounting a pair of axially spaced planet gears 88 and 89, respectively. Located between the planet gears 88 and 89 and in meshing relation therewith is a sun gear 90 carried at one end of a shaft'91 which also mounts an impeller 92 and rotates within aspider 93 secured to a mouth portion 94 of a compressor scroll or .casing generally designated by the numeral 95.

The planet gears further mesh with teeth 96 formed on the inner diameter of an annular flange portion 97 at the opposite axial end of the compressor scroll 95. The annular flange portion 97 with gear teeth 96 thereon accordingly functions as a ring gear, and as will now be noted, remain stationary with respect to the planet gears 88 and 89 and sun gear 90. *The compressor scroll or casing 95 is formed with, a

' volute portion 98 communicating with an angularly ardriven independently of the refrigerating unit A', or may be in the form of a plurality of fan blades 78' cast integral with compressor housing wall 27 or in any other suitable manner secured thereto. Thefan blades 78-may comprise relatively short length radial segments or may extend essentially entirely along the housing end Wall 27. The fan baldes 78 may also be of various shapes, and maybe tapered in width from the radial outward edge to the radial inward edge, as shown. It may thus be seen that ranged tubular portion 99 received at one end in a collar portion 100 formed in an opposite end wall 101 of the compressor housing 79. Arranged within the same end of the tubular portion 99 is an end section 62 of the condenser 19 constructed in the manner of Figure 1. 'As is shown in Figure 4, the impeller 92 is provided with blade portions 102 in the manner known in the art, and the spider93 is apertured as shown at 103 to provide a flow passage for refrigerant contained in compressor chamber 194 defined bythe housing 79, the refrigerant being com pressed by action of the impeller 92 and configuration of the interior of the compressor scroll 95.

- Rotation of the shaft 83 and compressor housing 79 rigidly secured thereto causes corresponding rotation of the connecting planet carrier 85 and travel of theplanet powerful streamsof air directed by'the fan blades 78 5 across the fins 26 on the evaporator chamber are sub stantially cooled, and th lower temperature "air is then or other area to be cooled. I a

It will now be apparent'from the foregoing suitably directed to an automobile passenger compartment descripgears '88 and -89in meshing relation withthe ring gear provided by the teeth 96 on the, annular. flange portion 97 of the-compressor scroll. The compressor scroll 95 and ring gear construction remain stationary by reason of an outof balance condition, and during rotation of the .planet gears 88 and 39 the sun gear is caused to tra vel in meshing relation therewith and drives the impe1ler 92 to compress the. refrigerant: received into the compressor tion that there is provideda heating or. cooling unit: of

compact iconstruction additionally featuring. maximum xefliciencyl-and minimum space requirements obtained by casing through the spider 93. It maybe seen upon ref: erence to Figure 5 that clockwiserotation ofthe corn;

-pressor casing or'housing 79 causes movement in the I same direction of, the 'planeticarrier and;p1anet;8ear j The fan blades 84 function as previ 88 and 89* supported by the carrier 85 I bymeansi of the shafts 86 and 87; Rotationin a clockwise direction of said planet gears 88' and 89 moves the sun gear 9%} in a counter-clockwise direction and effects counter-clockwise rotation of the impeller 92. It will now be apparent that the torque reaction on the stationary ring gear arrangement is counter-clockwise when the planet carrier 35 rotates clockwise. The torque reaction, however, on the compressor scroll 95 is clockwise under the conditions noted, and thereby the out of balance condition or weight of the compressor scroll need furnish only the difference between the torque reactions on the ring gear and compressor scroll as a restraining torque. Refrigerant compressed by the compressor casing 95 and impeller 92 therein is directed at a high pressure condition from the volute 98 through the tubular section 99 and into the condenser 19, wherein sensible heat is rejected by the refrigcrant from work done upon it during compression plus its latent heat of vaporization. The fluid then proseeds from the condenser 19 into the receiving chamber 23 and evaporator chamber 25, undergoing physical changes in its travel therethrough. The low pressure vapor from the the evaporator chamber is then directed through the passage 76 into the suction side of the compressor 104, and the cycle is repeated.

It may be seen from the foregoing that applicant has provided a-refrigeration or heating unit wherein the compressor, condenser and evaporator rotate as a single unit and provide a high coefiicient of performance with minimum space requirements. By arranging the condenser, receiver and evaporator in circumferentially stacked relation with. respect to one another greater efiiciency is promoted in both construction and operation. Motivation for the apparatus may be provided by a single source connecting with shafting at either end of the apparatus and in automotive applications, one end of the apparatus may connect with a power source to actuate said apparatus during movement of. the vehicle, while the opposite end of said apparatus may connect with an auxiliary power source which is employed when the main power source is not in use.

The apparatus herein disclosed is susceptible of wide variation in compressor construction to fulfill particular requirements. While two exemplary forms of compressor means are shown, there may also be employed a stationary cylinder depending from a shaft to restrain the same, an outer casingand the shaft rotating to recipro-' cate the piston in the cylinder. The latter arrangement may be found particularly suitable for the smaller installations. In addition, particular applications may require that a gyroscope be employed in connection with the compressor to assure an out of balance condition at all times. I

It is to be further noted from the foregoing description that a controlled flow of condensate into the evaporative heat exchange means is effected by a syphon device positioned with one end in communication with centrifugally impelled liquid refrigerant. Additionally, by effecting a forced air flow over the condenser and evaporator the rotating apparatus has utility as a source of either heated or cooled air for the automobile passenger compartment or other area in fluid communication with the apparatus. Various modifications may be effected in the structures herein disclosed without departing from the novel concepts of the present invention.

1 claim as my invention:

.1. A heat pump unit comprising, a rotary compressor housing and compressor means contained therewithin, an annular core member structurally connected for rotation with the compressor housing and having fins extending radially outwardly therefrom, a condenser in the core member and in fluid communication with the compressor means, an annular receiving chamber having one wall structurally connected for rotation with the finsiof the cor'e'member and'being influidcommunication with the condenser, andlan annular evaporating chamber having one wall common with the receiving chamber and being in fluid communication with the receiving chamber and compressor means.

2; A heat pump unit comprising, a rotary compressor housing. and compressor means contained therewithin, an'

annular core member. structurally connected for rota tion with the: compressor housing and having fins exthe core member and being in fluid communication with the condenser, an annular evaporating chamber having one wall common with the receiving chamber and being in fluid communication with the compressor means, and Syphon means carried by the common wall of the receiving and evaporating chambers and opening into said chambers to discharge centrifugally impelled fluid from the receiving chamber adjacent said common wall into the evaporating chamber radially outwardly of the common wall.

3. A heat pump unit comprising, a rotary compressor housing and compressor means contained therewithin, shaft means rigidly connected to said housing to impart rotation thereto, an annular core member integral with the compressor housing and having fins extending radially outwardly therefrom, a condenser embedded in the core member and in fluid communication With the compressor means, an annular receiving chamber having one wall integral with the fins of the core member and being in fluid communication with the condenser, an annular evaporating chamber having one wall common with the receiving chamber and being in fluid communication with the compressor means, and syphon means carried by the common wall of the receiving and evaporating chambers and opening into said chambers to discharge centrifugally impelled fluid from the re ceiving chamber adjacent said common wall into the evaporating. chamber radially outwardly of the common wall, the condenser being surrounded by the receiving chamber and the latter chamber by the evaporating chamber, and the path of flow of refrigerant being axially in one direction from the compressor means to the condenser, radially outwardly from the condenser to the receiving chamber and then to the evaporating chamber, and axially in the opposite direction from the evaporating chamber to the compressor housing interior.

4'. A heat pump unit comprising, a rotary compressor housing and compressor means contained therewithin, an annular core member integral with the compressor housing and having fins extending radially outwardly therefrom, a condenser in the core member and in fluid communication with the compressor means, an annular receiving chamber having one wall structurally connected for rotation with the fins of the core member,-

one of the fins being passaged with a restricted opening communicating at one end with the condenser and at the opposite end with the receiving chamber, an annular evaporating chamber having one wall common with the receiving chamber and being in fluid communication with the compressor means, and syphon means carried by the common wall of the receiving and evaporating chambers and opening into said chambers to discharge centrifugally impelled fluid from the receiving chamber adjacent said common wall into the evaporating chamber radially outwardly of the common wall.

5 In combination with a-condenser and evaporator,

the improvement which comprises, ,a rotary compressor 7 housing structurally connected with the condenser and evaporator to rotate therewith as a unit, and compres- 'sor: means within said housing; said compressor means comprising a volut'e compressor casing, shaft means within said casing, shaft-means within said casing, a stationary spider located at one end of the shaft means, a sun gear supported at the opposite end of the shaft, an impeller mounted between said. spider and sun gear, a pair of planet gears meshing with the sun gear, a ring gear formed on the casing interior meshing with the planet gears, and a planet carrier mounting the planet gears and secured to the interior of the compressor housing, rotation of the shaft and housing rigid thereon causing travel of the planet carrier and travel of the planet gears in meshing relation with the ring gear and sun gear to rotate the impeller, the compression casing and ring gear thereon remaining essentially stationary during said rotation.

6. A heating and cooling unit comprising, compressor means and a supporting shaft therefor connected to a power source to rotate said shaft and compressor means, condenser means and a supporting shaft therefor connected to a second power source to rotate the compressor means and condenser means as a unit when the first power source is not in use, and an evaporator means surrounding the condenser means and structurally connected to both the compressor means and condenser means whereby all means rotate as a unit upon rotation of either of the supporting shafts.

7. A heat pump unit hermetically sealed as a whole and rotatable as a whole about an axis for actuation thereof comprising, a generally cylindrical housing concentrio with, and rotatable about, said axis, a generally cylindrical condensing and evaporating second housing concentric with, and rotatable about, said axis, said assembly being axially spaced from, and structurally connected to, said compressor housing for rotation therewith and interconnected therewith for closed circuit fluid recirculation; said second housing having an inner axially extending condenser with an axially extending air passage for cooling air flow therepast and having an outer axially extending evaporator surrounding said condenser, said evaporator having air heat exchange fins thereon along its axial length,

8. A sealed heat pump unit rotatable about an axis as a whole for actuation thereof comprising, a first compressor housing having compressor means therein, a second condensing and evaporating'housing axially spaced from said first housing and connected thereto for rotation therewith and for fluid recirculation therethrough, said second housing comprising an inner condenser with an exposed surface for heat exchange to air flow and an outer evaporator with an exposed surface for heat exchange to air flow, and two blower means for said two air flows including radial blower blades connected in between said first and second housings.

9. A heat pump unit hermetically sealed as a whole and,

rotatable as a whole about an axis for actuation thereof comprising, a generally cylindrical compressor housing concentric with, and rotatable about, said axis, and.- a

generally cylindrical condensing and evaporating second housing concentric with, and rotatable about, said axis, said assembly being axially spaced from, and structurally connected to, said compressor housing for rotation there with and interconnected therewith for closed circuit fluid recirculating, said second housing having an inner condenser with a surface for heat'exchange toair flow and an outer evaporator with a surface for-heat exchange to air flow, said heat pump unit having two fan means to and second housings. 7 g

10. A rotatable heat pump unit comprising agenerally cylindrical compressor housing concentric with, and rotatable about, anaXis, and having compressor means therein, a generally cylindrical condensing and evaporating 10 V thereto for rotation about said axis and interconnected therewith for closed circuit fluid recirculation ,therethrough an inner condenser in said second housing having an axially extending surface for heat exchange to an air flow, an outer evaporator in said second housing around said condenser, said evaporator having an axially extending surface for heat exchange to a second air flow, and said heat pump unit including two rigidly connected fan means to induce said two heat exchange air flows.

11. In combination with a condenser and evaporator, the improvement which comprises shaft means, a rotary compressor housing rigidly supported by said shaft and structurally connected with the condenser and evaporator to rotate therewith as a unit, and compressor means Within said housing; said compressor means comprising an open-ended cylinder, transverse to, and centrally supported by said shaft for rotation with the compressor housing,

a pair of'oppositely acting, opposed and inwardly facing pistons reciprocably mounted in said cylinder, rotatable means carried by the outer end of each piston, and a stationary annular internal cam means surrounding said cylinder and actuatingly engaging said rotatable means of each said piston, said cam means having a radial wall during rotation of the compressor housing, condenser and evaporator and during actuation of said pistons thereby to effect refrigerant compression by movement between the two pistons.

12. In combination with a condenser and evaporator, the improvement which comprises a rotary compressor housing structurally connected to the condenser and evaporator to rotate therewith as a unit, and compressor means within said housing; said compressor means comprising an open-ended and transversely extending cylinder connected for rotation with the compressor housing, passage means along the axis of rotation to provide fluid communication between the condenser and compressor cylinder interior, the walls of the cylinder being passaged to provide inlet ports for refrigerant within the compressor housing, a pair of oppositely acting and inwardly facing pistons reciprocably mounted in said cylinder, and stationary annular internal cam means surrounding said cylinder actuatingly engaging the radially outer ends of said piston, and said cam means having a radial wall thickness relatively greater in one peripheral portion than in the remaining peripheral portions whereby said cam means is out of balance and remains essentially stationary during rotation of said compressor housing, condenser and evaporator and during =travel of the outer piston ends thereover to effect refrigerant compression by relative'movement between said pistons.

13. A heat pump unit hermetically sealed as a whole and rotatable as a whole for actuation thereof com- 7 prising a condenser, an evaporator and a compressor three relatively rotatable portions of which one is con-' nected vto said driven compr'e'ssorhousing, the second is housing structurally connected for rotation as a unit and drive means therefor in said compressor housing, said drive means comprising rotary planetary means having J connectedto said compressor means, and the third-isconinduce said two air flows one of which'fan means com .pr'ises radial blower blades connectedbetween said first nected to, andheld against rotation "by an unbalanced "weight means. 5

14,), heat pumpsunit hermetically sealed as aj whole and rotatable as a whole for actuation thereof comprising a 'condensen'an evaporator, and a compressor housing;

structurally connected for rotation as a unit and interconnected for fluid recirculation 'in a closed circuit there- 7 through, a relatively rotatablecompressor and drive and 1 speed increasing means therefor in said compressorlhous- 'ing,'said drive andlspeed increasing means comprising a planetary gearing set having three relativelyrotatable portions of which one is connected to said compressor housing, a second is connected to said rotatable compressor to drive it at a higher speed than said housing, and the third is connected to an unbalanced weight in said compressor housing to hold it against rotation by a torque less than the drive torque and equal to the difference between the drive torque and the rotary compressor torque.

15. A heat pump unit hermetically sealed as a Whole and rotatable as a whole about an aXis for actuation thereof comprising, a generally cylindrical compressor housing having compressor means therein and being concentric With, and rotatable about, said axis, and a generally cylindrical condensing and evaporating, second housing concentric With, and rotatable about, said axis,

References Cited in the file of this patent UNITED STATES PATENTS 983,010 Vinzent et al. Jan. 31, 1911 1,155,780 Andifiren et a1 Oct. 5, 1915 2,724,953 Justice Nov. 29, 1955 Justice Feb. 9, 1960 

